US20150275885A1 - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- US20150275885A1 US20150275885A1 US14/668,127 US201514668127A US2015275885A1 US 20150275885 A1 US20150275885 A1 US 20150275885A1 US 201514668127 A US201514668127 A US 201514668127A US 2015275885 A1 US2015275885 A1 US 2015275885A1
- Authority
- US
- United States
- Prior art keywords
- passage
- communication hole
- valve
- space
- discharge
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1066—Valve plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/122—Cylinder block
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1809—Controlled pressure
- F04B2027/1813—Crankcase pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
Definitions
- the present invention relates to a compressor.
- a compressor includes a cylinder block, a front housing, a rear housing, and a valve-forming plate or the like.
- the valve-forming plate is interposed between the cylinder block and the rear housing.
- the cylinder block forms a compression chamber inside a cylinder bore.
- the rear housing forms a discharge chamber toward which a refrigerant compressed in the compression chamber is discharged, and an accommodation chamber accommodating a check valve therein and communicating with the discharge chamber through the check valve.
- the compressor includes a discharge passage for delivering the refrigerant compressed in the compression chamber to an external device (a condenser, for example).
- the valve-forming plate is formed by an intake valve, a valve plate, a discharge valve and a retainer, and the discharge passage is formed in the rear housing, the valve-forming plate and the cylinder block.
- the valve-forming plate is provided with a communication hole functioning as a part of the discharge passage.
- the rear housing is provided with a passage for communicating the accommodation chamber accommodating the check valve therein with the communication hole formed in the valve-forming plate.
- the cylinder block is provided with a connection portion to be connected to an external device (a condenser, for example), and another passage for communicating the connection portion with the communication hole formed in the valve-forming plate.
- An object of the present invention is to provide a compressor capable of achieving a high flexibility in designing a discharge passage.
- a compressor which is provided with a compression chamber and a discharge passage and is configured to deliver a refrigerant compressed in the compression chamber to an external device through the discharge passage includes a cylinder block configured to form the compression chamber, a rear housing configured to form a discharge chamber toward which the refrigerant compressed in the compression chamber is discharged and an accommodation chamber accommodating a check valve therein and communicating with the discharge chamber through the check valve, and a valve-forming plate interposed between the cylinder block and the rear housing and including a communication hole which constitutes a part of the discharge passage.
- the rear housing includes a first passage extending from the accommodation chamber towards the communication hole of the valve-forming plate.
- the cylinder block includes a connection portion to be connected to the external device, an outlet space opening towards the connection portion, and a second passage extending from the outlet space towards the communication hole of the valve-forming plate.
- the discharge passage includes the discharge chamber, the accommodation chamber, the first passage, the communication hole, the second passage, and the outlet space.
- the flow passage area of the communication hole is larger than at least one of the flow passage area of the first passage and the flow passage area of the second passage.
- FIG. 1 is a sectional view illustrating a compressor according to a first embodiment
- FIG. 2 is a sectional view illustrating an enlarged discharge valve and an enlarged discharge passage of the compressor according to the first embodiment
- FIG. 3 is a perspective view illustrating a cylinder block, a valve-forming plate and a rear housing of the compressor according to the first embodiment in an exploded state;
- FIG. 4 is a bottom view schematically illustrating the compressor according to the first embodiment
- FIG. 5 is a bottom view for explaining the functions and effects of the compressor according to the first embodiment
- FIG. 6 is a sectional view illustrating an enlarged discharge passage of a compressor according to a second embodiment
- FIG. 7 is a sectional view illustrating an enlarged discharge passage of a compressor according to a third embodiment.
- FIG. 8 is a sectional view illustrating an enlarged discharge passage of a compressor according to a fourth embodiment.
- FIG. 1 is a sectional view illustrating a compressor 100 according to the first embodiment.
- the compressor 100 is a swash plate typed compressor having a variable capacity.
- the compressor 100 includes a compression chamber 1 r and a discharge passage 6 s, and is configured to deliver a refrigerant compressed in the compression chamber 1 r to an external device (such as a condenser) through the discharge passage 6 s.
- an external device such as a condenser
- the compression chamber 1 r is connected to the condenser through the discharge passage 6 s, the condenser is connected to an evaporator through an expansion valve, and the evaporator is connected to a suction chamber (suction chamber 5 a ).
- the compressor 100 includes a cylinder block 1 , a front housing 3 , a rear housing 5 and a valve-forming plate 2 .
- the front housing 3 is joined to the front end of the cylinder block 1
- the rear housing 5 is joined to the rear end of the cylinder block 1 through the valve-forming plate 2 .
- a plurality of cylinder bores lb are formed inside the cylinder block 1 .
- the cylinder block 1 and the front housing 3 form a crank chamber 9 .
- the cylinder block 1 has a shaft hole 1 h
- the front housing 3 has a shaft hole 3 h.
- the shaft holes 1 h and 3 h support a drive shaft 6 through the intermediary of a shaft-sealing units 9 a and shaft-bearing units 9 b and 9 c.
- a pulley 6 m is installed to the front housing 3 through a bearing device 3 b.
- the pulley 6 m is fixed to the drive shaft 6 , and a belt 6 n driven by a vehicular engine or motor is wound on the pulley 6 m.
- a lug plate 9 f and a swash plate 7 are provided inside the crank chamber 9 .
- the lug plate 9 f is press-fitted to the drive shaft 6 , and the drive shaft 6 is inserted into and penetrates the swash plate 7 .
- Bearing units 9 d and 9 e are provided between the lug plate 9 f and the front housing 3 .
- An inclination angle-reducing spring 8 a is provided between the lug plate 9 f and the swash plate 7 .
- the lug plate 9 f and the swash plate 7 are connected together by a link mechanism 7 c.
- a circlip 6 a is fixed to the drive shaft 6 .
- a return spring 8 b is provided between the circlip 6 a and the swash plate 7 .
- the plurality of cylinder bores 1 b each houses therein one piston 1 p.
- a pair of shoes 7 a and 7 b are provided between each piston 1 p and the swash plate 7 . The wobbling motion of the swash plate 7 is converted into the reciprocating movement of each piston 1 p by the shoes 7 a and 7 b.
- the valve-forming plate 2 is interposed between the rear end face of the cylinder block 1 and the front end surface of the rear housing 5 .
- the cylinder bore 1 b of the cylinder block 1 forms the compression chamber 1 r between the piston 1 p and the valve-forming plate 2 .
- the valve-forming plate 2 includes an intake valve, a valve plate, a discharge valve, a retainer and the like, and has a substantially plate-like shape as a whole.
- the valve-forming plate 2 is provided with a discharge port 2 p (see FIG. 2 ) and a suction port (not shown), and a peripheral part (a bulge portion 2 t illustrated in FIG. 3 ) of the valve-forming plate 2 is formed with a communication hole 2 h (see also FIG. 3 ) which constitutes a part of the discharge passage 6 s.
- a suction chamber 5 a, a discharge chamber 5 b, and an accommodation chamber 5 c are formed inside the rear housing 5 .
- the suction chamber 5 a is in communication with the compression chamber 1 r inside the cylinder bore 1 b through a suction port (not shown) formed to penetrate through the valve-forming plate 2 .
- the crank chamber 9 and the suction chamber 5 a are connected together by a passage 4 a.
- the crank chamber 9 and the discharge chamber 5 b are connected together by passages 4 b and 4 c.
- the rear housing 5 houses therein a capacity control valve 4 g.
- the capacity control valve 4 g is in communication with the passages 4 b and 4 c, and meanwhile is communication with the suction chamber 5 a through the intermediary of a pressure detecting passage 4 d.
- the capacity control valve 4 g based on a detected flow rate differential pressure or the like of the refrigerant gas in the pressure detecting passage 4 d, controls the passage 4 b and 4 c to open or close.
- the high-pressure refrigerant gas in the discharge chamber 5 b is supplied to the crank chamber 9 through the passages 4 b and 4 c. Adjusting the pressure in the crank chamber 9 to a desired value causes the inclination angle of the swash plate 7 to change, and thereby changes the discharge capacity to a desired one.
- the discharge chamber 5 b within the rear housing 5 is in communication with the compression chamber 1 r inside the cylinder bore 1 b through the discharge port 2 p which is formed to penetrate through the valve-forming plate 2 (see FIG. 2 ).
- the accommodation chamber 5 c is formed adjacent to the discharge chamber 5 b and accommodates therein the check valve 10 .
- the accommodation chamber 5 c (specifically, a part of the accommodation chamber 5 c located downstream than the check valve 10 ) communicates with the discharge chamber 5 b through the check valve 10 .
- FIG. 2 is a sectional view illustrating the enlarged check valve 10 and the enlarged discharge passage 6 s.
- the check valve 10 is provided with a valve seat 11 , a valve body 12 , a valve housing 13 and a spring 14 , and is press-installed inside the accommodation chamber 5 c.
- the valve seat 11 has a valve hole 11 h .
- the valve body 12 is configured to close the valve hole 11 h when being moved in the valve housing 13 along the direction towards the valve seat 11 , and to open the valve hole 11 h when being moved in the valve housing 13 along the direction away from the valve seat 11 .
- the valve housing 13 houses therein a spring 14 urging the valve body 12 towards the valve-closing direction.
- a side wall of the valve housing 13 is formed with a communication window 15 .
- FIG. 3 is a perspective view illustrating the cylinder block 1 , the valve-forming plate 2 and the rear housing 5 in an exploded state.
- the valve-forming plate 2 in FIG. 3 is illustrated as a single plate for the purpose of clarity and convenience in the drawing, and in fact, the valve-forming plate 2 includes the intake valve, the valve plate, the discharge valve, the retainer and the like (see FIG. 2 ).
- the rear housing 5 has an outer peripheral surface 5 s .
- the rear housing 5 is provided with a bulge portion 5 t bulging outward (radially outward).
- the outer peripheral surface 5 s of the rear housing 5 has a shape that bulges convexly outward (radially outward).
- the outer peripheral surface 5 s of the rear housing 5 has a cylindrical shape.
- the bulge portion 5 t constitutes a part of the rear housing 5 , and is integrally formed with the part of the rear housing 5 that forms the discharge chamber 5 b and the accommodation chamber 5 c.
- a first passage 5 d and a first space 5 e are formed inside the bulge portion 5 t .
- the part of the rear housing 5 that forms the discharge chamber 5 b and the accommodation chamber 5 c and the part of the rear housing 5 that forms the first passage 5 d and the first space 5 e are made of the same material (aluminum-based metal or the like).
- the first passage 5 d and the first space 5 e communicate with each other, and the first space 5 e is located at the downstream of the first passage 5 d in the flowing direction of the refrigerant.
- the first passage 5 d has for example a cylindrical shape, and extends towards a part where the communication hole 2 h of the valve-forming plate 2 to be described later is formed.
- the upstream end m 1 (see FIG. 2 ) of the first passage 5 d opens towards the accommodation chamber 5 c, and the downstream end m 2 (see FIG. 2 ) of the first passage 5 d opens towards the first space 5 e.
- the part of the rear housing 5 that forms the first space 5 e has a bottomed cylindrical shape.
- the first space 5 e is formed into a concave shape through a cutting process or the like performed on a part of an end face 5 j (see FIG. 3 ) of the rear housing 5 that joins to the valve-forming plate 2 .
- the first space 5 e has an opening in the end face 5 j.
- the first space 5 e is formed into a substantially cubic space extending in the direction indicated by an arrow AR 1 (see FIG. 3 ), and the flow passage area S 2 of the first space 5 e (see FIG. 2 ) is larger than the flow passage area S 1 of the first passage 5 d (see FIG. 2 ).
- the direction indicated by the arrow AR 1 corresponds to the circumferential direction of the rear housing 5 .
- the valve-forming plate 2 includes a disc portion 2 s (circular portion) and a bulge portion 2 t (another bulge portion) bulging outward (radially outward) from the outer peripheral edge of the disc portion 2 s.
- the outer peripheral edge of the valve-forming plate 2 has a shape that bulges convexly outward (radially outward).
- the outer peripheral edge of the valve-forming plate 2 has a circular shape.
- the communication hole 2 h is formed inside the bulge portion 2 t.
- the communication hole 2 h is formed into a substantially cubic space extending in the direction indicated by an arrow AR 2 (see FIG. 3 ).
- the direction indicated by the arrow AR 2 corresponds to the circumferential direction of the valve-forming plate 2 .
- the communication hole 2 h and the first space 5 e have substantially the same outer edge shape, and the flow passage area S 3 of the communication hole 2 h (see FIG. 2 ) is substantially the same as the flow passage area S 2 of the first space 5 e (see FIG. 2 ).
- the flow passage area S 3 of the communication hole 2 h is larger than the flow passage area S 1 of the first passage 5 d.
- the cylinder block 1 has an outer peripheral surface 1 s .
- the cylinder block 1 is provided with a bulge portion 1 t that bulges outward (radially outward) and a bulge portion 1 u that bulges outward further than the bulge portion 1 t .
- the outer peripheral surface 1 s of the cylinder block 1 has a shape that bulges convexly outward (radially outward).
- the outer peripheral surface 1 s of the cylinder block 1 has a cylindrical shape.
- the bulge portions 1 t and 1 u constitute a part of the cylinder block 1 , and are integrally formed with the part of the cylinder block 1 that forms the cylinder bores 1 b .
- a second space 1 c and a second passage 1 d are formed inside the bulge portion 1 t of the cylinder block 1 .
- An outlet space 1 e is formed inside the bulge portion 1 u .
- the part of the cylinder block 1 that forms the cylinder bores 1 b and the part of the cylinder block 1 that forms the second space 1 c , the second passage 1 d and the outlet space 1 e are made of the same material (aluminum-based metal or the like).
- the second space 1 c , the second passage 1 d and the outlet space 1 e communicate with each other.
- the second space 1 c is located at the upstream of the second passage 1 d
- the outlet space 1 e is located at the downstream of the second passage 1 d .
- the second passage 1 d and the outlet space 1 e each has for example a cylindrical shape.
- the second passage 1 d extends from the outlet space 1 e towards the part of the valve-forming plate 2 where the communication hole 2 h is formed.
- the upstream end n 1 (see FIG. 2 ) of the second passage 1 d opens towards the second space 1 c
- the downstream end n 2 see FIG.
- connection portion 1 f is a site to be connected to an external device 20 (see FIG. 2 ) such as a condenser.
- the part of the cylinder block 1 that forms the second space 1 c has a bottomed cylindrical shape.
- the second space 1 c is formed into a concave shape through a cutting process or the like performed on a part of an end face 1 j (see FIG. 3 ) of the cylinder block 1 that joins to the valve-forming plate 2 .
- the second space 1 c has an opening in the end face 1 j .
- the second space 1 c is formed into a substantially cubic space extending in the direction indicated by an arrow AR 3 (see FIG.
- the flow passage area S 4 of the second space 1 c (see FIG. 2 ) is larger than the flow passage area S 5 of the second passage 1 d (see FIG. 2 ).
- the direction indicated by the arrow AR 3 corresponds to the circumferential direction of the cylinder block 1 .
- the flow passage area S 4 of the second space 1 c (see FIG. 2 ) is substantially the same as the flow area S 3 of the communication hole 2 h (see FIG. 2 ). In other words, the flow passage area S 3 of the communication hole 2 h is larger than the flow passage area S 5 of the second passage 1 d.
- the part of the cylinder block 1 that forms the outlet space 1 e also has a bottomed cylindrical shape.
- the outlet space 1 e is formed into a concave shape through a cutting process or the like performed on a part of the end face of the cylinder block 1 that forms the connection portion 1 f .
- the outlet space 1 e has an opening in the connection portion 1 f .
- the outlet space 1 e is formed into a substantially cylindrical space, and the flow passage area S 6 of the outlet space 1 e (see FIG. 2 ) is larger than the flow passage area S 5 of the second passage 1 d (see FIG. 2 ).
- the discharge passage 6 s in the present embodiment includes the discharge chamber 5 b, the accommodation chamber 5 c, the first passage 5 d, the first space 5 e, the communication hole 2 h, the second space 1 c , the second passages 1 d , and the outlet space 1 e .
- the compressor 100 is configured to deliver the refrigerant compressed in the compression chamber 1 r to an external device (such as a condenser) through the discharge passage 6 s, and thereby it can function as for example a part of the refrigerant circuit.
- FIG. 4 is a bottom view schematically illustrating the compressor 100 , and the compressor 100 is illustrated as being viewed from the side of the rear housing 5 .
- the external device 20 such as a condenser or the like is connected to the connection portion 1 f of the compressor 100 through a connection pipe.
- the position to dispose the external device 20 may be changed according to, for example, the specifications of the external device 20 and/or the specifications of a vehicle where the compressor 100 and the external device 20 are mounted. Since it is possible for the compressor 100 of the present embodiment to achieve a high flexibility in designing the discharge passage 6 s, it can flexibly cope with the changes in the abovementioned specifications, which will be described in detail hereinafter.
- the flow passage area S 3 of the communication hole 2 h (see FIG. 2 ) provided in the valve-forming plate 2 is larger than the flow passage area S 1 of the first passage 5 d (see FIG. 2 ) provided in the rear housing 5 .
- the downstream end m 2 of the first passage 5 d can be freely positioned within the range indicated by an arrow DR 1 .
- the downstream end m 2 of the first passage 5 d is positioned within the range indicated by the arrow DR 1 , as long as the downstream end m 2 of the first passage 5 d is opened towards the communication hole 2 h, it is possible for the first passage 5 d to communicate the accommodation chamber 5 c with the communication hole 2 h. Therefore, since the downstream end m 2 of the first passage 5 d can be freely positioned within the range indicated by the arrow DR 1 , the installation range (such as the installation angle and the installation position) of the first passage 5 d for communicating with the communication hole 2 h can be widened, and thereby it is possible to achieve a high flexibility in designing the discharge passage 6 s.
- the flow passage area S 3 of the communication hole 2 h (see FIG. 2 ) provided in the valve-forming plate 2 is larger than the flow passage area S 5 of the second passage 1 d (see FIG. 2 ) provided in the bulge portion 1 t of the cylinder block 1 .
- the upstream end n 1 of the second passage 1 d can be freely positioned within the range indicated by an arrow DR 2 .
- the upstream end n 1 of the second passage 1 d is positioned within the range indicated by the arrow DR 2 , as long as the upstream end n 1 of the second passage 1 d is opened towards the communication hole 2 h, it is possible for the second passage 1 d to communicate the communication hole 2 h with the outlet space 1 e (connection portion 1 f ). Therefore, since the upstream end n 1 of the second passage 1 d can be freely positioned within the range indicated by the arrow DR 2 , the installation range (such as the installation angle and the installation position) of the second passage 1 d for communicating with the communication hole 2 h can be widened, and thereby it is possible to achieve a high flexibility in designing the discharge passage 6 s.
- the flow passage area S 6 of the outlet space 1 e (see FIG. 2 ) is larger than the flow passage area S 5 of the second passage 1 d (see FIG. 2 ).
- the downstream end n 2 of the second passage 1 d (see also FIG. 2 ) can be freely positioned within the range indicated by an arrow DR 3 .
- downstream end n 2 of the second passage 1 d is positioned within the range indicated by the arrow DR 3 , as long as the downstream end n 2 of the second passage 1 d is opened towards the outlet space 1 e , it is possible for the second passage 1 d to communicate the communication hole 2 h with the outlet space 1 e (connection portion 1 f ). Therefore, since the downstream end n 2 of the second passage 1 d can be freely positioned within the range indicated by the arrow DR 3 , the installation range (such as the installation angle and the installation position) of the second passage 1 d for communicating with the communication hole 2 h can be widened, and thereby it is possible to achieve a high flexibility in designing the discharge passage 6 s.
- the first space 5 e (see FIG. 2 ) is provided between the communication hole 2 h and the first passage 5 d.
- the flow passage area S 2 of the first space 5 e (see FIG. 2 ) is larger than the flow passage area Si of the first passage 5 d (see FIG. 2 ).
- the refrigerant contracts and expands when passing through the accommodation chamber 5 c, the first passage 5 d and the first space 5 e.
- the accommodation chamber 5 c, the first passage 5 d and the first space 5 e can function as a muffler chamber.
- the second space 1 c (see FIG. 2 ) is provided between the communication hole 2 h and the second passage 1 d
- the outlet space 1 e (see FIG. 2 ) is provided between the connection portion 1 f and the second passage 1 d
- the flow passage area S 4 of the second space 1 c (see FIG. 2 ) is larger than the flow passage area S 5 of the second passage 1 d (see FIG. 2 ).
- the flow passage area S 6 of the outlet space 1 e (see FIG. 2 ) is larger than the flow passage area S 5 of the second passage 1 d (see FIG. 2 ).
- the refrigerant contracts and expands when passing through the second space 1 c , the second passage 1 d and the outlet space 1 e .
- the second space 1 c , the second passage 1 d and the outlet space 1 e can function as a muffler chamber.
- the compressor 100 is provided with a bulge portion (bulge portion 1 t , 2 t and/or 5 t ) that bulges outward, and the communication hole 2 h provided in the valve-forming plate 2 is located within the bulge portion.
- the bulge portion 1 t is formed integral with the cylinder block 1
- the bulge portion 5 t is formed integral with the rear housing 5 . According to this configuration, compared with the case where a member is provided separately so as to join the bulge portion to the cylinder block 1 and/or the rear housing 5 , it is possible to reduce the manufacturing cost.
- the first space 5 e (see FIG. 2 ) is not formed in the rear housing 5
- the second space 1 c (see FIG. 2 ) is not formed in the cylinder block 1
- the first passage 5 d formed in the rear housing 5 is in direct communication with the communication hole 2 h of the valve-forming plate 2
- second passage 1 d formed in the cylinder block 1 is also in direct communication with the communication hole 2 h of the valve-forming plate 2 .
- the flow passage area S 3 of the communication hole 2 h is larger than the flow passage area S 1 of the first passage 5 d, and the flow passage area S 3 of the communication hole 2 h is also larger than the flow passage area S 5 of the second passage 1 d .
- the installation range (such as the installation angle and the installation position) for communicating the first passage 5 d and the second passage 1 d with the communication hole 2 h can be widened, it is possible to achieve a high flexibility in designing the discharge passage 6 s.
- the first space 5 e may be formed in the rear housing 5 .
- the second space 1 c may be formed in the cylinder block 1 .
- the flow passage area S 3 of the communication hole 2 h is not configured as being larger than the flow passage area S 5 of the second passage 1 d .
- the flow passage area S 3 of the communication hole 2 h is configured as being larger than the flow passage area S 1 of the first passage 5 d. According to this configuration, since the installation range (such as the installation angle and the installation position) for communicating the first passage 5 d with the communication hole 2 h can be widened, it is possible to achieve a high flexibility in designing the discharge passage 6 s.
- the flow passage area S 3 of the communication hole 2 h is not configured as being larger than the flow passage area S 1 of the first passage 5 d.
- the flow passage area S 3 of the communication hole 2 h is configured as being larger than the flow passage area S 5 of the second passage 1 d . According to this configuration, since the installation range (such as the installation angle and the installation position) for communicating the second passage 1 d with the communication hole 2 h can be widened, it is possible to achieve a high flexibility in designing the discharge passage 6 s.
Abstract
Description
- This non-provisional application is based on Japanese Patent Application No. 2014-066325 filed on Mar. 27, 2014 with the Japan Patent Office, the entire contents of which are hereby incorporated by reference.
- 1. Field of the Invention
- The present invention relates to a compressor.
- 2. Description of the Background Art
- A compressor includes a cylinder block, a front housing, a rear housing, and a valve-forming plate or the like. The valve-forming plate is interposed between the cylinder block and the rear housing. The cylinder block forms a compression chamber inside a cylinder bore. The rear housing forms a discharge chamber toward which a refrigerant compressed in the compression chamber is discharged, and an accommodation chamber accommodating a check valve therein and communicating with the discharge chamber through the check valve.
- As disclosed in Japanese Patent Laying-Open No. 2000-346218, the compressor includes a discharge passage for delivering the refrigerant compressed in the compression chamber to an external device (a condenser, for example). In the compressor disclosed by the document, the valve-forming plate is formed by an intake valve, a valve plate, a discharge valve and a retainer, and the discharge passage is formed in the rear housing, the valve-forming plate and the cylinder block.
- In the case where the discharge passage is formed in the rear housing, the valve-forming plate and the cylinder block, the valve-forming plate is provided with a communication hole functioning as a part of the discharge passage. The rear housing is provided with a passage for communicating the accommodation chamber accommodating the check valve therein with the communication hole formed in the valve-forming plate. The cylinder block is provided with a connection portion to be connected to an external device (a condenser, for example), and another passage for communicating the connection portion with the communication hole formed in the valve-forming plate.
- Conventionally, it was difficult to increase flexibility in design of these passages. Specifically, in a conventional compressor, since the communication hole provided in the valve-forming plate has a small dimension (flow passage area), there is only limited installation range (such as the installation angle and the installation position) inside which these passages may communicate with the small communication hole.
- An object of the present invention is to provide a compressor capable of achieving a high flexibility in designing a discharge passage.
- A compressor which is provided with a compression chamber and a discharge passage and is configured to deliver a refrigerant compressed in the compression chamber to an external device through the discharge passage includes a cylinder block configured to form the compression chamber, a rear housing configured to form a discharge chamber toward which the refrigerant compressed in the compression chamber is discharged and an accommodation chamber accommodating a check valve therein and communicating with the discharge chamber through the check valve, and a valve-forming plate interposed between the cylinder block and the rear housing and including a communication hole which constitutes a part of the discharge passage. The rear housing includes a first passage extending from the accommodation chamber towards the communication hole of the valve-forming plate. The cylinder block includes a connection portion to be connected to the external device, an outlet space opening towards the connection portion, and a second passage extending from the outlet space towards the communication hole of the valve-forming plate. The discharge passage includes the discharge chamber, the accommodation chamber, the first passage, the communication hole, the second passage, and the outlet space. The flow passage area of the communication hole is larger than at least one of the flow passage area of the first passage and the flow passage area of the second passage.
- The foregoing and other objects, features, aspects and advantages of the present invention will become more apparent from the following detailed description of the present invention when taken in conjunction with the accompanying drawings.
-
FIG. 1 is a sectional view illustrating a compressor according to a first embodiment; -
FIG. 2 is a sectional view illustrating an enlarged discharge valve and an enlarged discharge passage of the compressor according to the first embodiment; -
FIG. 3 is a perspective view illustrating a cylinder block, a valve-forming plate and a rear housing of the compressor according to the first embodiment in an exploded state; -
FIG. 4 is a bottom view schematically illustrating the compressor according to the first embodiment; -
FIG. 5 is a bottom view for explaining the functions and effects of the compressor according to the first embodiment; -
FIG. 6 is a sectional view illustrating an enlarged discharge passage of a compressor according to a second embodiment; -
FIG. 7 is a sectional view illustrating an enlarged discharge passage of a compressor according to a third embodiment; and -
FIG. 8 is a sectional view illustrating an enlarged discharge passage of a compressor according to a fourth embodiment. - Embodiments in accordance with the present invention will be described hereinafter with reference to the drawings. Unless otherwise specified, the scope of the present invention is not limited to the number, the amount or the like cited in the embodiments to be described below. The same components and corresponding components are assigned with the same reference numerals, and the description may not be repeated.
- (Compressor 100)
-
FIG. 1 is a sectional view illustrating acompressor 100 according to the first embodiment. Thecompressor 100 is a swash plate typed compressor having a variable capacity. To be described in detail hereinafter, thecompressor 100 includes acompression chamber 1 r and adischarge passage 6 s, and is configured to deliver a refrigerant compressed in thecompression chamber 1 r to an external device (such as a condenser) through thedischarge passage 6 s. In the case where thecompressor 100 is employed in a vehicular air conditioner for example, thecompression chamber 1 r is connected to the condenser through thedischarge passage 6 s, the condenser is connected to an evaporator through an expansion valve, and the evaporator is connected to a suction chamber (suction chamber 5 a). - Specifically, the
compressor 100 includes acylinder block 1, afront housing 3, arear housing 5 and a valve-formingplate 2. Thefront housing 3 is joined to the front end of thecylinder block 1, and therear housing 5 is joined to the rear end of thecylinder block 1 through the valve-formingplate 2. - A plurality of cylinder bores lb are formed inside the
cylinder block 1. Thecylinder block 1 and thefront housing 3 form acrank chamber 9. Thecylinder block 1 has ashaft hole 1 h, and thefront housing 3 has ashaft hole 3 h. Theshaft holes drive shaft 6 through the intermediary of a shaft-sealing units 9 a and shaft-bearingunits pulley 6 m is installed to thefront housing 3 through abearing device 3 b. Thepulley 6 m is fixed to thedrive shaft 6, and abelt 6 n driven by a vehicular engine or motor is wound on thepulley 6 m. - A
lug plate 9 f and aswash plate 7 are provided inside thecrank chamber 9. Thelug plate 9 f is press-fitted to thedrive shaft 6, and thedrive shaft 6 is inserted into and penetrates theswash plate 7.Bearing units lug plate 9 f and thefront housing 3. An inclination angle-reducingspring 8 a is provided between thelug plate 9 f and theswash plate 7. Thelug plate 9 f and theswash plate 7 are connected together by alink mechanism 7 c. - A
circlip 6 a is fixed to thedrive shaft 6. Areturn spring 8 b is provided between thecirclip 6 a and theswash plate 7. The plurality of cylinder bores 1 b each houses therein onepiston 1 p. A pair ofshoes piston 1 p and theswash plate 7. The wobbling motion of theswash plate 7 is converted into the reciprocating movement of eachpiston 1 p by theshoes - The valve-forming
plate 2 is interposed between the rear end face of thecylinder block 1 and the front end surface of therear housing 5. The cylinder bore 1 b of thecylinder block 1 forms thecompression chamber 1 r between thepiston 1 p and the valve-formingplate 2. The valve-formingplate 2 includes an intake valve, a valve plate, a discharge valve, a retainer and the like, and has a substantially plate-like shape as a whole. To be described in detail hereinafter, the valve-formingplate 2 is provided with adischarge port 2 p (seeFIG. 2 ) and a suction port (not shown), and a peripheral part (abulge portion 2 t illustrated inFIG. 3 ) of the valve-formingplate 2 is formed with acommunication hole 2 h (see alsoFIG. 3 ) which constitutes a part of thedischarge passage 6 s. - A
suction chamber 5 a, adischarge chamber 5 b, and anaccommodation chamber 5 c are formed inside therear housing 5. Thesuction chamber 5 a is in communication with thecompression chamber 1 r inside the cylinder bore 1 b through a suction port (not shown) formed to penetrate through the valve-formingplate 2. Thecrank chamber 9 and thesuction chamber 5 a are connected together by apassage 4 a. Thecrank chamber 9 and thedischarge chamber 5 b are connected together bypassages - The
rear housing 5 houses therein acapacity control valve 4 g. Thecapacity control valve 4 g is in communication with thepassages suction chamber 5 a through the intermediary of apressure detecting passage 4 d. Thecapacity control valve 4 g, based on a detected flow rate differential pressure or the like of the refrigerant gas in thepressure detecting passage 4 d, controls thepassage discharge chamber 5 b is supplied to the crankchamber 9 through thepassages crank chamber 9 to a desired value causes the inclination angle of theswash plate 7 to change, and thereby changes the discharge capacity to a desired one. - The
discharge chamber 5 b within therear housing 5 is in communication with thecompression chamber 1 r inside the cylinder bore 1 b through thedischarge port 2 p which is formed to penetrate through the valve-forming plate 2 (seeFIG. 2 ). Theaccommodation chamber 5 c is formed adjacent to thedischarge chamber 5 b and accommodates therein thecheck valve 10. Theaccommodation chamber 5 c (specifically, a part of theaccommodation chamber 5 c located downstream than the check valve 10) communicates with thedischarge chamber 5 b through thecheck valve 10. - (Check Valve 10)
-
FIG. 2 is a sectional view illustrating theenlarged check valve 10 and theenlarged discharge passage 6 s. Thecheck valve 10 is provided with avalve seat 11, avalve body 12, avalve housing 13 and aspring 14, and is press-installed inside theaccommodation chamber 5 c. Thevalve seat 11 has avalve hole 11 h. Thevalve body 12 is configured to close thevalve hole 11 h when being moved in thevalve housing 13 along the direction towards thevalve seat 11, and to open thevalve hole 11 h when being moved in thevalve housing 13 along the direction away from thevalve seat 11. - The
valve housing 13 houses therein aspring 14 urging thevalve body 12 towards the valve-closing direction. A side wall of thevalve housing 13 is formed with acommunication window 15. When the valve is opened, the refrigerant from thevalve hole 11 h flows into theaccommodation chamber 5 c (specifically, a part of theaccommodation chamber 5 c located downstream than the check valve 10) through thecommunication window 15. - (
Discharge Passage 6 s) -
FIG. 3 is a perspective view illustrating thecylinder block 1, the valve-formingplate 2 and therear housing 5 in an exploded state. The valve-formingplate 2 inFIG. 3 is illustrated as a single plate for the purpose of clarity and convenience in the drawing, and in fact, the valve-formingplate 2 includes the intake valve, the valve plate, the discharge valve, the retainer and the like (seeFIG. 2 ). - (
First Passage 5 d andFirst Space 5 e) - Referring to
FIGS. 2 and 3 , therear housing 5 has an outerperipheral surface 5 s. Therear housing 5 is provided with abulge portion 5 t bulging outward (radially outward). In the part where thebulge portion 5 t is formed, the outerperipheral surface 5 s of therear housing 5 has a shape that bulges convexly outward (radially outward). In the other part where thebulge portion 5 t is not formed, the outerperipheral surface 5 s of therear housing 5 has a cylindrical shape. - The
bulge portion 5 t constitutes a part of therear housing 5, and is integrally formed with the part of therear housing 5 that forms thedischarge chamber 5 b and theaccommodation chamber 5 c. Afirst passage 5 d and afirst space 5 e are formed inside thebulge portion 5 t. The part of therear housing 5 that forms thedischarge chamber 5 b and theaccommodation chamber 5 c and the part of therear housing 5 that forms thefirst passage 5 d and thefirst space 5 e are made of the same material (aluminum-based metal or the like). - The
first passage 5 d and thefirst space 5 e communicate with each other, and thefirst space 5 e is located at the downstream of thefirst passage 5 d in the flowing direction of the refrigerant. Thefirst passage 5 d has for example a cylindrical shape, and extends towards a part where thecommunication hole 2 h of the valve-formingplate 2 to be described later is formed. The upstream end m1 (seeFIG. 2 ) of thefirst passage 5 d opens towards theaccommodation chamber 5 c, and the downstream end m2 (seeFIG. 2 ) of thefirst passage 5 d opens towards thefirst space 5 e. - The part of the
rear housing 5 that forms thefirst space 5 e has a bottomed cylindrical shape. Thefirst space 5 e is formed into a concave shape through a cutting process or the like performed on a part of anend face 5 j (seeFIG. 3 ) of therear housing 5 that joins to the valve-formingplate 2. In the case where therear housing 5, the valve-formingplate 2 and the like are in an exploded state (the state illustrated inFIG. 3 ), thefirst space 5 e has an opening in theend face 5 j. In the present embodiment, thefirst space 5 e is formed into a substantially cubic space extending in the direction indicated by an arrow AR1 (seeFIG. 3 ), and the flow passage area S2 of thefirst space 5 e (seeFIG. 2 ) is larger than the flow passage area S1 of thefirst passage 5 d (seeFIG. 2 ). The direction indicated by the arrow AR1 corresponds to the circumferential direction of therear housing 5. - (
Communication Hole 2 h) - As illustrated in
FIG. 3 , the valve-formingplate 2 includes adisc portion 2 s (circular portion) and abulge portion 2 t (another bulge portion) bulging outward (radially outward) from the outer peripheral edge of thedisc portion 2 s. In the part where thebulge portion 2 t is formed, the outer peripheral edge of the valve-formingplate 2 has a shape that bulges convexly outward (radially outward). In the other part where thebulge portion 2 t is not formed, the outer peripheral edge of the valve-formingplate 2 has a circular shape. - The
communication hole 2 h is formed inside thebulge portion 2 t. In the present embodiment, thecommunication hole 2 h is formed into a substantially cubic space extending in the direction indicated by an arrow AR2 (seeFIG. 3 ). The direction indicated by the arrow AR2 corresponds to the circumferential direction of the valve-formingplate 2. Thecommunication hole 2 h and thefirst space 5 e have substantially the same outer edge shape, and the flow passage area S3 of thecommunication hole 2 h (seeFIG. 2 ) is substantially the same as the flow passage area S2 of thefirst space 5 e (seeFIG. 2 ). In other words, the flow passage area S3 of thecommunication hole 2 h is larger than the flow passage area S1 of thefirst passage 5 d. - (
Second Space 1 c,Second Passage 1 d andOutlet Space 1 e) - Referring to
FIGS. 2 and 3 , thecylinder block 1 has an outerperipheral surface 1 s. Thecylinder block 1 is provided with abulge portion 1 t that bulges outward (radially outward) and abulge portion 1 u that bulges outward further than thebulge portion 1 t. In the part where thebulge portions peripheral surface 1 s of thecylinder block 1 has a shape that bulges convexly outward (radially outward). In the other part where thebulge portions peripheral surface 1 s of thecylinder block 1 has a cylindrical shape. - The
bulge portions cylinder block 1, and are integrally formed with the part of thecylinder block 1 that forms the cylinder bores 1 b. Asecond space 1 c and asecond passage 1 d are formed inside thebulge portion 1 t of thecylinder block 1. Anoutlet space 1 e is formed inside thebulge portion 1 u. The part of thecylinder block 1 that forms the cylinder bores 1 b and the part of thecylinder block 1 that forms thesecond space 1 c, thesecond passage 1 d and theoutlet space 1 e are made of the same material (aluminum-based metal or the like). - The
second space 1 c, thesecond passage 1 d and theoutlet space 1 e communicate with each other. In the flowing direction of the refrigerant, thesecond space 1 c is located at the upstream of thesecond passage 1 d, and theoutlet space 1 e is located at the downstream of thesecond passage 1 d. Thesecond passage 1 d and theoutlet space 1 e each has for example a cylindrical shape. Thesecond passage 1 d extends from theoutlet space 1 e towards the part of the valve-formingplate 2 where thecommunication hole 2 h is formed. The upstream end n1 (seeFIG. 2 ) of thesecond passage 1 d opens towards thesecond space 1 c, and the downstream end n2 (seeFIG. 2 ) of thesecond passage 1 d opens towards theoutlet space 1 e. The downstream end of theoutlet space 1 e opens towards aconnection portion 1 f. Theconnection portion 1 f is a site to be connected to an external device 20 (seeFIG. 2 ) such as a condenser. - The part of the
cylinder block 1 that forms thesecond space 1 c has a bottomed cylindrical shape. Thesecond space 1 c is formed into a concave shape through a cutting process or the like performed on a part of anend face 1 j (seeFIG. 3 ) of thecylinder block 1 that joins to the valve-formingplate 2. In the case where thecylinder block 1, the valve-formingplate 2 and the like are in an exploded state (the state illustrated inFIG. 3 ), thesecond space 1 c has an opening in theend face 1 j. In the present embodiment, thesecond space 1 c is formed into a substantially cubic space extending in the direction indicated by an arrow AR3 (seeFIG. 3 ), and the flow passage area S4 of thesecond space 1 c (seeFIG. 2 ) is larger than the flow passage area S5 of thesecond passage 1 d (seeFIG. 2 ). The direction indicated by the arrow AR3 corresponds to the circumferential direction of thecylinder block 1. In the present embodiment, the flow passage area S4 of thesecond space 1 c (seeFIG. 2 ) is substantially the same as the flow area S3 of thecommunication hole 2 h (seeFIG. 2 ). In other words, the flow passage area S3 of thecommunication hole 2 h is larger than the flow passage area S5 of thesecond passage 1 d. - The part of the
cylinder block 1 that forms theoutlet space 1 e also has a bottomed cylindrical shape. Theoutlet space 1 e is formed into a concave shape through a cutting process or the like performed on a part of the end face of thecylinder block 1 that forms theconnection portion 1 f. In a state where theexternal device 20 is detached (through detaching a connection pipe or the like) from theconnection portion 1 f, theoutlet space 1 e has an opening in theconnection portion 1 f. In the present embodiment, theoutlet space 1 e is formed into a substantially cylindrical space, and the flow passage area S6 of theoutlet space 1 e (seeFIG. 2 ) is larger than the flow passage area S5 of thesecond passage 1 d (seeFIG. 2 ). - Referring again to
FIGS. 1 and 2 , thedischarge passage 6 s in the present embodiment includes thedischarge chamber 5 b, theaccommodation chamber 5 c, thefirst passage 5 d, thefirst space 5 e, thecommunication hole 2 h, thesecond space 1 c, thesecond passages 1 d, and theoutlet space 1 e. Thecompressor 100 is configured to deliver the refrigerant compressed in thecompression chamber 1 r to an external device (such as a condenser) through thedischarge passage 6 s, and thereby it can function as for example a part of the refrigerant circuit. - (Functions and Effects)
-
FIG. 4 is a bottom view schematically illustrating thecompressor 100, and thecompressor 100 is illustrated as being viewed from the side of therear housing 5. Theexternal device 20 such as a condenser or the like is connected to theconnection portion 1 f of thecompressor 100 through a connection pipe. The position to dispose theexternal device 20 may be changed according to, for example, the specifications of theexternal device 20 and/or the specifications of a vehicle where thecompressor 100 and theexternal device 20 are mounted. Since it is possible for thecompressor 100 of the present embodiment to achieve a high flexibility in designing thedischarge passage 6 s, it can flexibly cope with the changes in the abovementioned specifications, which will be described in detail hereinafter. - As described in the above, the flow passage area S3 of the
communication hole 2 h (seeFIG. 2 ) provided in the valve-formingplate 2 is larger than the flow passage area S1 of thefirst passage 5 d (seeFIG. 2 ) provided in therear housing 5. As illustrated inFIG. 4 , when providing thefirst passage 5 d in therear housing 5, the downstream end m2 of thefirst passage 5 d (see alsoFIG. 2 ) can be freely positioned within the range indicated by an arrow DR1. Even though the downstream end m2 of thefirst passage 5 d is positioned within the range indicated by the arrow DR1, as long as the downstream end m2 of thefirst passage 5 d is opened towards thecommunication hole 2 h, it is possible for thefirst passage 5 d to communicate theaccommodation chamber 5 c with thecommunication hole 2 h. Therefore, since the downstream end m2 of thefirst passage 5 d can be freely positioned within the range indicated by the arrow DR1, the installation range (such as the installation angle and the installation position) of thefirst passage 5 d for communicating with thecommunication hole 2 h can be widened, and thereby it is possible to achieve a high flexibility in designing thedischarge passage 6 s. - Similarly, the flow passage area S3 of the
communication hole 2 h (seeFIG. 2 ) provided in the valve-formingplate 2 is larger than the flow passage area S5 of thesecond passage 1 d (seeFIG. 2 ) provided in thebulge portion 1 t of thecylinder block 1. As illustrated inFIG. 4 , when providing thesecond passage 1 d in thecylinder block 1, the upstream end n1 of thesecond passage 1 d (see alsoFIG. 2 ) can be freely positioned within the range indicated by an arrow DR2. Even though the upstream end n1 of thesecond passage 1 d is positioned within the range indicated by the arrow DR2, as long as the upstream end n1 of thesecond passage 1 d is opened towards thecommunication hole 2 h, it is possible for thesecond passage 1 d to communicate thecommunication hole 2 h with theoutlet space 1 e (connection portion 1 f). Therefore, since the upstream end n1 of thesecond passage 1 d can be freely positioned within the range indicated by the arrow DR2, the installation range (such as the installation angle and the installation position) of thesecond passage 1 d for communicating with thecommunication hole 2 h can be widened, and thereby it is possible to achieve a high flexibility in designing thedischarge passage 6 s. - In the present embodiment, the flow passage area S6 of the
outlet space 1 e (seeFIG. 2 ) is larger than the flow passage area S5 of thesecond passage 1 d (seeFIG. 2 ). As illustrated inFIG. 4 , when providing thesecond passage 1 d in thecylinder block 1, the downstream end n2 of thesecond passage 1 d (see alsoFIG. 2 ) can be freely positioned within the range indicated by an arrow DR3. Even though the downstream end n2 of thesecond passage 1 d is positioned within the range indicated by the arrow DR3, as long as the downstream end n2 of thesecond passage 1 d is opened towards theoutlet space 1 e, it is possible for thesecond passage 1 d to communicate thecommunication hole 2 h with theoutlet space 1 e (connection portion 1 f). Therefore, since the downstream end n2 of thesecond passage 1 d can be freely positioned within the range indicated by the arrow DR3, the installation range (such as the installation angle and the installation position) of thesecond passage 1 d for communicating with thecommunication hole 2 h can be widened, and thereby it is possible to achieve a high flexibility in designing thedischarge passage 6 s. - As illustrated in
FIG. 5 , for example, even in the case where it is necessary to change the position of theconnection portion 1 f along direction indicated by an arrow DR4, it is possible for therear housing 5 and the valve-forming plate 2 (not shown) to share a common structure illustrated inFIG. 4 . Similarly, even in the case where it is necessary to change the position of theaccommodation chamber 5 c in accordance with the specifications of therear housing 5, it is possible for thecylinder block 1 and the valve-forming plate 2 (not shown) to share a common structure illustrated inFIG. 4 . Therefore, the adoption of the ideas contained in thecompressor 100 improves the versatility of components, which thereby makes it possible to reduce the manufacturing cost. - In the present embodiment, the
first space 5 e (seeFIG. 2 ) is provided between thecommunication hole 2 h and thefirst passage 5 d. The flow passage area S2 of thefirst space 5 e (seeFIG. 2 ) is larger than the flow passage area Si of thefirst passage 5 d (seeFIG. 2 ). The refrigerant contracts and expands when passing through theaccommodation chamber 5 c, thefirst passage 5 d and thefirst space 5 e. Thus, theaccommodation chamber 5 c, thefirst passage 5 d and thefirst space 5 e can function as a muffler chamber. - In the present embodiment, the
second space 1 c (seeFIG. 2 ) is provided between thecommunication hole 2 h and thesecond passage 1 d, and theoutlet space 1 e (seeFIG. 2 ) is provided between theconnection portion 1 f and thesecond passage 1 d. The flow passage area S4 of thesecond space 1 c (seeFIG. 2 ) is larger than the flow passage area S5 of thesecond passage 1 d (seeFIG. 2 ). The flow passage area S6 of theoutlet space 1 e (seeFIG. 2 ) is larger than the flow passage area S5 of thesecond passage 1 d (seeFIG. 2 ). The refrigerant contracts and expands when passing through thesecond space 1 c, thesecond passage 1 d and theoutlet space 1 e. Thus, thesecond space 1 c, thesecond passage 1 d and theoutlet space 1 e can function as a muffler chamber. - In the present embodiment, the
compressor 100 is provided with a bulge portion (bulge portion communication hole 2 h provided in the valve-formingplate 2 is located within the bulge portion. Thebulge portion 1 t is formed integral with thecylinder block 1, and thebulge portion 5 t is formed integral with therear housing 5. According to this configuration, compared with the case where a member is provided separately so as to join the bulge portion to thecylinder block 1 and/or therear housing 5, it is possible to reduce the manufacturing cost. - In a
compressor 101 illustrated inFIG. 6 , thefirst space 5 e (seeFIG. 2 ) is not formed in therear housing 5, and thesecond space 1 c (seeFIG. 2 ) is not formed in thecylinder block 1. Thefirst passage 5 d formed in therear housing 5 is in direct communication with thecommunication hole 2 h of the valve-formingplate 2, andsecond passage 1 d formed in thecylinder block 1 is also in direct communication with thecommunication hole 2 h of the valve-formingplate 2. - In the
compressor 101, the flow passage area S3 of thecommunication hole 2 h is larger than the flow passage area S1 of thefirst passage 5 d, and the flow passage area S3 of thecommunication hole 2 h is also larger than the flow passage area S5 of thesecond passage 1 d. According to this configuration, since the installation range (such as the installation angle and the installation position) for communicating thefirst passage 5 d and thesecond passage 1 d with thecommunication hole 2 h can be widened, it is possible to achieve a high flexibility in designing thedischarge passage 6 s. In addition to the configuration of the second embodiment, similar to the first embodiment, thefirst space 5 e may be formed in therear housing 5. In addition to the configuration of the second embodiment, similar to the first embodiment, thesecond space 1 c may be formed in thecylinder block 1. - In a
compressor 102 illustrated inFIG. 7 , the flow passage area S3 of thecommunication hole 2 h is not configured as being larger than the flow passage area S5 of thesecond passage 1 d. However, the flow passage area S3 of thecommunication hole 2 h is configured as being larger than the flow passage area S1 of thefirst passage 5 d. According to this configuration, since the installation range (such as the installation angle and the installation position) for communicating thefirst passage 5 d with thecommunication hole 2 h can be widened, it is possible to achieve a high flexibility in designing thedischarge passage 6 s. - In a
compressor 103 illustrated inFIG. 8 , the flow passage area S3 of thecommunication hole 2 h is not configured as being larger than the flow passage area S1 of thefirst passage 5 d. However, the flow passage area S3 of thecommunication hole 2 h is configured as being larger than the flow passage area S5 of thesecond passage 1 d. According to this configuration, since the installation range (such as the installation angle and the installation position) for communicating thesecond passage 1 d with thecommunication hole 2 h can be widened, it is possible to achieve a high flexibility in designing thedischarge passage 6 s. - Although the present invention has been described and illustrated in detail, it is clearly understood that the same is by way of illustration and example only and is not to be taken by way of limitation, the scope of the present invention being interpreted by the terms of the appended claims.
Claims (6)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014066325A JP6164135B2 (en) | 2014-03-27 | 2014-03-27 | Compressor |
JP2014-066325 | 2014-03-27 |
Publications (2)
Publication Number | Publication Date |
---|---|
US20150275885A1 true US20150275885A1 (en) | 2015-10-01 |
US9810209B2 US9810209B2 (en) | 2017-11-07 |
Family
ID=54067052
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/668,127 Expired - Fee Related US9810209B2 (en) | 2014-03-27 | 2015-03-25 | Compressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US9810209B2 (en) |
JP (1) | JP6164135B2 (en) |
KR (1) | KR101690862B1 (en) |
CN (1) | CN104948422B (en) |
DE (1) | DE102015104619B4 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160320114A1 (en) * | 2013-12-26 | 2016-11-03 | Sanden Holdings Corporation | Flow rate measuring device and variable displacement compressor |
Citations (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5262068A (en) * | 1991-05-17 | 1993-11-16 | Millipore Corporation | Integrated system for filtering and dispensing fluid having fill, dispense and bubble purge strokes |
US5871337A (en) * | 1995-10-26 | 1999-02-16 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash-plate compressor with leakage passages through the discharge valves of the cylinders |
US5971716A (en) * | 1995-06-09 | 1999-10-26 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor having a muffler and a capacity control valve mounted thereto |
US6015269A (en) * | 1996-12-10 | 2000-01-18 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
US6149397A (en) * | 1998-03-06 | 2000-11-21 | Toyoda Automatic Loom Works, Ltd. | Pressure pulsations reducing compressor |
US6227812B1 (en) * | 1997-03-13 | 2001-05-08 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Refrigerant circuit and compressor |
US6241483B1 (en) * | 1998-11-12 | 2001-06-05 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
US6435848B1 (en) * | 1999-06-07 | 2002-08-20 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable capacity type compressor with check valve |
US6568921B2 (en) * | 2000-01-29 | 2003-05-27 | Bitzer Kuehlmaschinenbau Gmbh | Refrigerant compressor |
US20040016346A1 (en) * | 2002-02-13 | 2004-01-29 | Klockner Khs, Inc. | Self-contained beverage proportioner unit |
US20050031456A1 (en) * | 2002-08-30 | 2005-02-10 | Sokichi Hibino | Swash plate type variable displacement compressor |
US20090173094A1 (en) * | 2006-04-06 | 2009-07-09 | Yukihiko Taguchi | Air conditioner |
US20090246041A1 (en) * | 2006-07-19 | 2009-10-01 | Sanden Corporation | Displacement control valve of a variable displacement compressor |
US20100260621A1 (en) * | 2009-04-10 | 2010-10-14 | Panasonic Corporation | Hermetic compressor |
US20120215514A1 (en) * | 2003-09-29 | 2012-08-23 | Pathwork Diagnostics, Inc. | Systems and methods for detecting biological features |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3301570B2 (en) | 1993-12-27 | 2002-07-15 | 株式会社豊田自動織機 | Reciprocating compressor |
JP3588851B2 (en) * | 1995-03-17 | 2004-11-17 | 株式会社豊田自動織機 | Reciprocating compressor |
JPH09287564A (en) | 1996-04-23 | 1997-11-04 | Zexel Corp | Reciprocating compressor |
JP3697782B2 (en) | 1996-07-08 | 2005-09-21 | 株式会社豊田自動織機 | Compressor muffler structure |
JP4066563B2 (en) | 1999-06-07 | 2008-03-26 | 株式会社豊田自動織機 | Check valve |
KR100659570B1 (en) | 2003-02-18 | 2006-12-19 | 한라공조주식회사 | Compressor |
JPWO2004088139A1 (en) | 2003-03-28 | 2006-07-06 | 株式会社ヴァレオサーマルシステムズ | Reciprocating compressor |
JP2006077731A (en) | 2004-09-13 | 2006-03-23 | Sanden Corp | Reciprocating compressor |
KR101165947B1 (en) | 2006-05-01 | 2012-07-18 | 한라공조주식회사 | Variable capacity type swash plate type compressor |
JP2009293386A (en) * | 2008-06-02 | 2009-12-17 | Toyota Industries Corp | Compressor |
JP5325041B2 (en) * | 2009-07-30 | 2013-10-23 | サンデン株式会社 | Reciprocating compressor |
CN202326090U (en) * | 2011-11-16 | 2012-07-11 | 上海三电贝洱汽车空调有限公司 | Exhaust silencing structure for compressors |
JP5595458B2 (en) | 2012-09-26 | 2014-09-24 | 東海ゴム工業株式会社 | Vibration isolator |
-
2014
- 2014-03-27 JP JP2014066325A patent/JP6164135B2/en not_active Expired - Fee Related
-
2015
- 2015-03-20 KR KR1020150038705A patent/KR101690862B1/en active IP Right Grant
- 2015-03-25 US US14/668,127 patent/US9810209B2/en not_active Expired - Fee Related
- 2015-03-25 CN CN201510132291.4A patent/CN104948422B/en not_active Expired - Fee Related
- 2015-03-26 DE DE102015104619.9A patent/DE102015104619B4/en not_active Expired - Fee Related
Patent Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5262068A (en) * | 1991-05-17 | 1993-11-16 | Millipore Corporation | Integrated system for filtering and dispensing fluid having fill, dispense and bubble purge strokes |
US5971716A (en) * | 1995-06-09 | 1999-10-26 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor having a muffler and a capacity control valve mounted thereto |
US5871337A (en) * | 1995-10-26 | 1999-02-16 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash-plate compressor with leakage passages through the discharge valves of the cylinders |
US6015269A (en) * | 1996-12-10 | 2000-01-18 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
US6227812B1 (en) * | 1997-03-13 | 2001-05-08 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Refrigerant circuit and compressor |
US6149397A (en) * | 1998-03-06 | 2000-11-21 | Toyoda Automatic Loom Works, Ltd. | Pressure pulsations reducing compressor |
US6241483B1 (en) * | 1998-11-12 | 2001-06-05 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
US6435848B1 (en) * | 1999-06-07 | 2002-08-20 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable capacity type compressor with check valve |
US6568921B2 (en) * | 2000-01-29 | 2003-05-27 | Bitzer Kuehlmaschinenbau Gmbh | Refrigerant compressor |
US20040016346A1 (en) * | 2002-02-13 | 2004-01-29 | Klockner Khs, Inc. | Self-contained beverage proportioner unit |
US20050031456A1 (en) * | 2002-08-30 | 2005-02-10 | Sokichi Hibino | Swash plate type variable displacement compressor |
US20120215514A1 (en) * | 2003-09-29 | 2012-08-23 | Pathwork Diagnostics, Inc. | Systems and methods for detecting biological features |
US20090173094A1 (en) * | 2006-04-06 | 2009-07-09 | Yukihiko Taguchi | Air conditioner |
US20090246041A1 (en) * | 2006-07-19 | 2009-10-01 | Sanden Corporation | Displacement control valve of a variable displacement compressor |
US20100260621A1 (en) * | 2009-04-10 | 2010-10-14 | Panasonic Corporation | Hermetic compressor |
US8323001B2 (en) * | 2009-04-10 | 2012-12-04 | Panasonic Corporation | Hermetic compressor |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160320114A1 (en) * | 2013-12-26 | 2016-11-03 | Sanden Holdings Corporation | Flow rate measuring device and variable displacement compressor |
Also Published As
Publication number | Publication date |
---|---|
US9810209B2 (en) | 2017-11-07 |
DE102015104619B4 (en) | 2018-11-29 |
KR20150112817A (en) | 2015-10-07 |
KR101690862B1 (en) | 2016-12-28 |
CN104948422A (en) | 2015-09-30 |
DE102015104619A1 (en) | 2015-10-01 |
JP6164135B2 (en) | 2017-07-19 |
JP2015190334A (en) | 2015-11-02 |
CN104948422B (en) | 2017-05-03 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US9670914B2 (en) | Check valve for compressor | |
JP4429931B2 (en) | Opening adjustment valve | |
EP1953385A2 (en) | Double-headed swash plate compressor | |
JP2007120408A (en) | Compressor | |
JP4606433B2 (en) | Variable capacity swash plate compressor | |
US9810209B2 (en) | Compressor | |
US20190032648A1 (en) | Variable displacement swash plate type compressor | |
US20150252797A1 (en) | Variable-Capacity Compressor | |
US20080120991A1 (en) | Compressor having a mechanism for separating and recovering lubrication oil | |
CN110318970B (en) | Piston type compressor | |
EP1983191B1 (en) | Variable displacement-type clutchless compressor | |
JP6879252B2 (en) | Variable capacity swash plate compressor | |
US20090238698A1 (en) | Reciprocal Compressor | |
JP6469994B2 (en) | Compressor | |
US20150023812A1 (en) | Variable displacement compressor with single-head pistons | |
JP2014118923A (en) | Compressor | |
JP6192369B2 (en) | Reciprocating compressor | |
US20160252084A1 (en) | Variable displacement swash plate type compressor | |
JP2006077731A (en) | Reciprocating compressor | |
JP6747813B2 (en) | Compressor | |
JP2021038703A (en) | Reciprocation type compressor | |
JP4498988B2 (en) | Opening adjustment valve | |
JP2014125994A (en) | Piston type compressor | |
KR101177294B1 (en) | Variable capacity type swash plate type compressor | |
JP2016176418A (en) | Compressor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KONDO, HISAYA;SAEKI, AI;SUZUKI, YASUSHI;AND OTHERS;REEL/FRAME:035252/0976 Effective date: 20150313 |
|
STCF | Information on status: patent grant |
Free format text: PATENTED CASE |
|
FEPP | Fee payment procedure |
Free format text: MAINTENANCE FEE REMINDER MAILED (ORIGINAL EVENT CODE: REM.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
LAPS | Lapse for failure to pay maintenance fees |
Free format text: PATENT EXPIRED FOR FAILURE TO PAY MAINTENANCE FEES (ORIGINAL EVENT CODE: EXP.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
STCH | Information on status: patent discontinuation |
Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362 |
|
FP | Lapsed due to failure to pay maintenance fee |
Effective date: 20211107 |